ES2604712T3 - Vaporizable refrigerator, adiabatic refrigerator or humidification unit and their manufacturing method - Google Patents

Abstract

Vaporizable refrigerator, adiabatic refrigerator or humidification unit comprising: a thermal exchange matrix (30) defining a single flow channel and comprising a plurality of generally flat sheets (32, 34) comprising a water retention material, a relationship arranged spaced apart, substantially parallel and a plurality of spacers (44) located between adjacent sheets to maintain their distance relationship, each sheet defines a main plane with a flow direction and a transverse direction, a housing (4) with the minus an air inlet (6), an air outlet (8), the array located in the housing; a fan arrangement (14) for directing air through the die in the flow direction; and a water source (12) for the humidification of the matrix, characterized in that the sheets comprise bands (36) that extend in a band length in the transverse direction and are separated from each neighboring band in the direction of flow and each band is compensated from the main plane by a distance that is different from that of its neighbor.

Description

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Vaporizable refrigerator, adiabatic refrigerator or humidification unit and method of manufacturing thereof Background of the invention

1. Field of the invention

[0001] The present invention relates to a thermal exchange matrix of the type that can be used as an adiabatic humidifier to introduce moisture into a fluid flow.

The invention also relates to methods of manufacturing such devices.

An array of this type can operate to provide adiabatic cooling for domestic use and can also be used for humidification in combination with conventional air conditioning and heating systems.

It can also be used to remove moisture from an air stream in combination with a suitable desiccant.

2. Description of related techniques

[0002] Thermal exchange devices in one form or another are present in virtually every device and process.

The performance of an action invariably implies the release of energy in the form of heat.

If not required, heat will often be released to the environment by an appropriate heat conduction surface provided, e.g. ex. with cooling fins.

If the amount of heat is excessive or if it can be used for useful uses, a specific heat exchanger can be provided to transport the heat out, e.g. ex. to another system.

The thermal exchange can also occur between different media: - gas, liquid and solid media can be interconnected in all combinations, according to the required performance.

[0003] Adiabatic systems, which act by evaporation of a liquid, usually water, in a stream of air are also known.

Such systems are not heat exchangers in the strictest sense, since they primarily do not cause heat to enter or leave the system.

In fact, they merely serve to change the temperature of the air stream while increasing its enthalpy only by the adequate heat of the added water.

As water evaporates in the air stream, the latent heat of evaporation of this water is provided by the cooling of the air stream.

This cooling method can be very effective for relatively hot, dry air.

[0004] Conventional adiabatic refrigerators are described in US3792841 and US 5143658.

Such devices generally comprise a matrix formed by stacks of corrugated plates placed on top of each other, so that the corrugations in adjacent layers are angled with respect to each other. The plates can be formed of various materials but the resin-reinforced organic or fibrous inorganic materials are the most common.

The plates are supported by a housing or rack that can provide input and output connections to guide an air current through the battery.

An irrigation arrangement serves to continuously or intermittently apply water or other evaporable liquid to the plates.

In operation, the air to be cooled passes through the battery.

Assuming that the air is not completely saturated, it will absorb aqueous vapor from the plates.

In this way, the air temperature drops to the so-called wet bulb temperature, which is the minimum theoretical.

For the given operating conditions, the efficiency of such devices can be determined by the input energy required to conduct the air flow through the battery.

In fact, this is the only significant external energy required and is largely determined by the total flow resistance of the cell and the speed of the air flow.

A major problem with the prior art devices is that to optimize efficiency, they tend to become relatively bulky.

[0005] In addition to adiabatic cooling, similarly constructed devices are also used to dampen air currents for other purposes.

In particular, in integrated heating, ventilation and air conditioning (HVAC) systems it is often desirable to increase the absolute humidity of the air for comfort purposes.

In particular, during the winter months, heating systems tend to cause the air to become relatively dry.

This can lead to respiratory problems, static electricity and other discomforts.

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It would be desirable to add moisture in an effective manner without increasing the volume of the HVAC installation.

[0006] An important distinction from previous devices on conventional heat exchangers is that they can interact with only one media stream.

This avoids complex input and output collectors and there is generally a small need to consider the thermal conductivity of the matrix.

Conventional air for aerating heat exchangers operates in transverse or counterflow flow with heat transfer that takes place between primary and secondary channels, which must be sealed from each other, e.g. ex. by heat conduction walls.

An important design consideration is the way in which an adequate heat transfer coefficient for the conduction walls is achieved.

Another consideration is how multiple interlaced channels are connected to input and output collectors.

[0007] Another class of heat exchangers is the heat recovery wheel.

Such devices use latent and suitable heat exchange means in the form of a matrix that provides air passages through which an air stream can be directed using a fan or blower.

The matrices hold a desiccant material that can absorb moisture and can take a variety of forms, such as a fibrous mesh or honeycomb.

A type of honeycomb matrix is formed by a plurality of spaced apart, substantially parallel layers of a sheet material, particularly alternating layers of a corrugated sheet material and a flat sheet material.

In the latter case, the corrugations are generally parallel and provide a plurality of axially extending passageways that extend along the depth of the wheel.

Such devices are described in US 4769053 and US 5542968.

Different materials have been proposed for matrix construction including aluminum and fibrous materials. Considerable attention has also been given to the optimized use of desiccant coatings.

However, a particular disadvantage of such wheels is their total volume.

This is generally related to the volume of material required for effective thermal exchange and the need for an effective flow passage area that will not lead to a significant pressure drop and associated high power consumption by the fan.

[0008] Many other forms of thermal exchange construction have been proposed in the past for several different purposes.

US 4147210 discloses a thermal screen exchanger comprising alternating filters and spacers.

The filters have been made of a conductive material, such as copper or aluminum in the form of a mesh.

[0009] Therefore, it would be desirable to improve existing designs, not only in terms of matrix volume for a given performance, but also in terms of the energy efficiency of flow through the device.

Brief Summary of the Invention

[0010] According to the invention, a thermal exchange matrix is provided defining a flow channel and comprising a plurality of flat sheets generally comprising a water retention material, arranged in a spaced, substantially parallel relationship, each sheet defines a main plane having a flow direction and a transverse direction, where the sheets comprise bands that extend in a band length in the transverse direction and are separated from each neighboring band in the flow direction and each band is compensated from the plane principal for a distance that is different from that of its neighbor.

It is believed that the resulting matrix considerably achieves a higher thermal exchange capacity per unit volume and, moreover, it is believed to have a higher efficiency in terms of flow resistance at air velocities, generally found in HVAC applications.

In the present context, by distance relationship it is understood merely that the main planes of each sheet are distanced from each other.

Thus, adjacent leaf bands can come into contact with each other and can help achieve spacing function.

In addition, although reference is made to flat sheets, it can be understood that these refer to their local arrangement and are not intended to be limiting in the general form of the matrix, which in use can be adapted to any appropriate form.

However, in general, the sheets will be flat at least in the flow direction and flat or curved in the transverse direction, as described below.

[0011] Although various configurations and orientations of the bands can be considered, however, in general the bands will generally be parallel to the flow direction.

Without intending to impose any theory, it is believed that an arrangement of all or most of the bands to be in the direction of the flow is advantageous in reducing the pressure drop through the heat exchanger.

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[0012] According to the present invention, the thermal exchange matrix may form a single flow channel.

It is understood that this means that, although spacers may be present, they do not divide the flow into hermetically isolated streams.

In addition, the flow channel defined by the matrix has a flow width in the transverse direction of at least a plurality of band lengths.

[0013] Although it is believed that the principle is applicable to sheets having offset bands for two different positions, it is believed that the device offers improved performance when the bands are compensated from the main plane, at least, to four different positions.

So that there is no doubt, in the present context, the zero compensation position is also considered a position that represents a band that is in the main plane of the sheet.

It is believed that the provision of offset bands for a plurality of positions is particularly advantageous in the case of evaporative cooling.

As will be discussed in more detail below, it is believed that the provision of bands in a plurality of compensation positions reduces the development of a laminar boundary layer within a stream of air flowing past the bands.

By reducing such a layer, a better water absorption of the surfaces of the bands is achieved and this successively leads to more efficient evaporation cooling

[0014] Preferably, the bands are compensated for positions above and below the main plane that allow a balanced distribution of material.

This may be of importance in a manufacturing process in the reduction of distortion.

In this context too, it has been discovered that it is convenient that the bands can be partially compensated for a first position and partially compensated for a second position.

In this way, the lengths of the bands in a given row of bands can be made so that all are equal to each other.

In this context, a distinction can be made between the length and the absolute length of a band.

The absolute length of a band is measured as the distance along the contour of the band between the points at which the band is connected to the sheet.

The length can be the direct distance between these two points.

In a preferred embodiment, the length of each band is about 10 mm while the absolute length can be about 12 mm.

By forming each of the fins with the same absolute length, at least partially, distortions in the plate due to the shape of the fins in the plate can be avoided.

[0015] To optimize the flow characteristics, each band is preferably distanced in the flow direction of a subsequent band with the same compensation of at least three times the bandwidth, more preferably, at least five times this width.

Not intending to impose any theory, it is believed that the flow is repeatedly interrupted by each band and the limited length of the band in the flow direction limits the development of the boundary layer.

According to this theory, the bands are arranged in the matrix and each band has a chosen position

carefully regarding your neighbors.

The position of each band in the matrix is chosen taking into account the following considerations.

[0016] It is believed that as a media stream, for example gas, passes over a band, a boundary layer is created

Gradually in the flow on the surface of the band, this creates what is known as laminar flow.

Since the speed within this limit layer is less than outside, it acts as an insulating layer that reduces a thermal transfer between the main body of the media and the band.

The result is a reduction in thermal transfer, since the medium flows along the length of the band.

In the case of a vaporizable refrigerator, it is believed that this boundary layer produces a layer of air with high humidity on the web surface.

This layer has a reduced capacity to absorb water due to its high humidity.

It also prevents less humid air from the main body of the air stream that reaches the band surface for other water absorption.

It can be the same case in reverse for heat recovery wheels and such devices.

In this case, the boundary layer can prevent moisture in the air flow that comes into good contact with the matrix material and its desiccant coating.

Therefore, the presence of such a boundary layer is disadvantageous because it reduces water absorption in vaporizable refrigerators and prevents moisture adsorption in desiccant devices.

[0017] To reduce the development of laminar flow in the heat exchanger, due to the creation of a boundary layer on the band surfaces, the bands are limited in length in the flow direction.

In theory, the band should not be longer than the length required for a boundary layer to grow to its full thickness on the band surface.

Once the air or media flow is beyond the band, the laminar flow gradually returns to turbulent regime.

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Taking this into consideration, the bands that are in a row in the direction of flow are properly distanced, so that when the means reach the leading edge of a downstream band, the laminar flow created by an upstream band will return sufficiently to turbulent flow. , so that a good thermal transfer can occur again.

Also, this downstream band is limited in length in the flow direction and is sufficiently distanced from another downstream band, so that turbulent flow is restored before the means reach the next downstream band.

In this way, the flow of laminar insulation is sufficiently avoided and a good thermal transfer between the means and bands is obtained and / or a good water absorption of the web surface is achieved.

According to a preferred form of the invention, the bands have a width of between 1 mm and 5 mm, preferably between 1.5 mm and 3.0 mm.

In one embodiment, the bands have a width of approximately 2.0 mm.

In general, all bands will be of the same width although this does not have to be the case and variable width bands can be used, e.g. ex. in different areas of the matrix.

[0018] According to another preferred embodiment, the separation, which is the distance between the front edge of a band and the front edge of a band that follows immediately in the flow direction is at least three times the bandwidth.

More preferably, this can be at least five bandwidths.

[0019] In addition to the previous consideration, the closest bands on an adjacent sheet should be sufficiently spaced apart to avoid excessive interference between the boundary layers of these closest bands.

Using these considerations, a matrix of sheets with bands can be stacked together, whereby the rows of bands are sufficiently distanced in the flow direction to avoid a laminar flow and the closest bands in adjacent layers are sufficiently distanced in the perpendicular direction to the flow direction to avoid excessive limit layer interference.

[0020] In one embodiment of the matrix, a plurality of spacers can be placed between adjacent sheets to keep their relationship distanced.

The spacers can also provide additional functionality, such as stiffness, mutual fixation of the layers, separation in the flow channels or regions and liquid supply.

However, according to an important aspect of the invention, the sheets can be stacked or rolled together without the use of spacers.

In this case, the compensation of the individual bands may be sufficient to keep the sheets apart.

[0021] In another embodiment of the invention, the bands are arranged in a plurality of rows extending in the direction of flow, each row is separated from an adjacent row by a band-free zone.

The band-free zone can ensure a degree of stability of the sheet to the extent that it defines a continuous piece of sheet that is not cut or otherwise deformed.

The band-free zone can also serve as a location for spacers.

[0022] According to an important aspect of the invention, the bands are provided with a water retention surface, preferably, on both surfaces thereof.

The water retention elements, as part of the band surface, such as a hardened surface, can be achieved by etching or similar surface treatment of the bands to make them more hydraulic in nature.

[0023] The water retention surface may alternatively be a separate layer that, for example, is coated or adhered on the bands.

In this aspect, the bands for use of adiabatic humidification or cooling can be distinguished from those used in indirect evaporation cooling.

In the latter case, it was generally considered necessary to have certain areas of the heat exchange surface free of any coating to facilitate direct heat transfer.

In the previous case, full coverage of the bands may be preferred.

In the past, it has been discovered that cementing materials such as Portland cement are highly desirable for use as water retention layers.

Alternatively, fibrous materials can be used.

[0024] In a preferred embodiment, a flexible water retention surface is provided on the sheet in the form of a laminate.

By providing a flexible water retention surface, the desired properties such as the spatial distribution of the liquid retention surface can be imparted to the sheet prior to formation.

Then the bands can be conveniently formed in the desired shape.

In a desirable embodiment, the water retention surface has an open structure so that in use, a thermal exchange medium can directly contact the band surface through the

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Open structure of the water retention layer.

In this way, the ability of the heat exchanger to transfer both thermal heat and latent heat to a fluid medium, flowing over it, is improved.

The open structure may comprise spaces between the fibers of a fibrous material that forms the water retention surface.

Such fibrous material can be a woven or non-woven layer that has an open structure.

[0025] The fibrous material can be attached to the sheet or bands by adhesives or other similar methods.

Preferably, the adhesive and the fibrous material should be such that delamination did not occur in the formation of the sheet in a desired shape.

Where the adhesive is used, the adhesive can be chosen to improve the properties of the web or the water retention layer.

Thus the adhesive can be chosen to have water retention properties or heat conduction properties or both and thus it can be considered to be part of any of these layers.

[0026] A preferred embodiment of the invention has a water retention surface comprising material that has been printed, sprayed or transferred onto the bands.

This printed material can be hydrophilic to retain water or can be provided in a model that acts to retain water by surface tension or capillary action.

Such a model may for example comprise isolated regions of material, the isolated regions are distanced by a distance that allows water retention while leaving parts of the underlying band open to the air flow.

Instead of or in addition to isolated regions of material, interlocking regions that provide the desired water retention can also be provided.

The impression of a material on the web surfaces can be produced by the inkjet printing.

[0027] According to a particular embodiment of the invention, the sheet comprises an aluminum layer.

In fact, the sheet can be predominantly aluminum p. ex. cover with water retention layers on both of its surfaces.

The sheet may have a thickness of between 50 and 300 microns, preferably between 75 and 150 microns.

For an aluminum based sheet, a thickness of aluminum material of about 70 microns sufficient to provide optimum strength and stability to the bands has been discovered.

If aluminum is used, it may preferably be coated with suitable lacquers to prevent corrosion.

It is understood that although aluminum offers advantages in terms of production, it may not necessarily be required for heat conduction purposes.

For example, other materials can also be used to form the matrix, in particular plastics and non-metallic materials.

[0028] Most preferably, the thermal exchange matrix, according to the invention, comprises a plurality of sheets of similar dimensions stacked together to form a block as a structure.

Alternatively, it may comprise one or more sheets wound together to form a cylindrical or annular structure.

The exact form will depend on the intended use and the manufacture of considerations, however, it has been found that a dimension in the flow direction of about 100 mm is sufficient for most HVAC.

In addition, the density of the sheets can be established so that a total surface area of the matrix between 500 m2 / m3 and 800 m2 / m3 is achieved, preferably around 650 m2 / m3.

In this preferred construction, the spacing between adjacent sheets is about 2.0 mm, but this can generally be between 1 mm and 5 mm, preferably between 1.5 mm and 3.0 mm.

[0029] The invention also relates to a thermal exchange sheet for the formation of such a matrix.

The sheet comprises bands that each extend in a band length in the transverse direction and are separated from each neighboring band in the flow direction, whereby each band is compensated from the main plane by a distance that is different from the from your neighbor.

It has been found that such a sheet is highly versatile in the formation of thermal exchange matrices in various shapes and configurations.

[0030] The invention also relates to a method of manufacturing such a thermal exchange matrix or sheet, comprising: providing a supply of sheet material with first and second water retention surfaces; passing the sheet material through a cutting station to cut the sheet to form a plurality of bands, each band has a band length that defines a transverse direction and each band is separated by the cut of each neighboring band in a direction flow; and pass the cutting blade through a training station to compensate each band from a main plane of the blade for a distance that is different from that of its neighbor.

[0031] The method is particularly applicable for a soft ringed aluminum sheet that shows stability

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necessary and strength, and can be easily cut and formed in the manner described.

Preferably, the sheet has a thickness of between 50 and 300 microns, preferably between 75 and 150 microns, including any coating or water retention provisions.

[0032] According to the inventive method, the sheet is fed in the transverse direction through rollers that are incorporated into the cutting station and the forming station.

Then, the worked sheet can be formed in a matrix by separating sheet sections and stacking the sections to form a stack with multiple layers.

Alternatively, the sheet can be rolled to form a roll with multiple layers.

Spacers can be inserted as necessary between the multiple layers to maintain their respective spacings or otherwise improve stability.

[0033] According to a further aspect of the invention, a vaporizable refrigerator, adiabatic refrigerator or humidification unit may comprise such a heat exchange matrix as described above, retained in a housing with at least one air inlet, one air outlet and a fan arrangement for directing air through the die in the flow direction.

Additionally, it may have provided a source of water for the humidification of the matrix.

The device can also be used for air purification or otherwise the elimination of odors, dust and other undesirable substances from an air flow.

In a preferred form, realized as an adiabatic refrigerator comprising a water source for the humidification of the matrix, the bands generally extend vertically and the flow channel generally extends horizontally, the water source is arranged to supply water to an upper side of the plurality of sheets, so that water can flow down along the bands.

Such a configuration allows an optimal distribution of water below and through the matrix.

In particular, in this configuration, the spacers provided to maintain a distance between adjacent sheets should not extend in the direction of flow since this would prevent the downward flow of water. Preferably, spacing by small dots or drops of adhesive or a suitable polymer between adjacent sheets is provided.

The points can have a maximum dimension of about 1 cm.

[0034] According to an alternative aspect, a heat recovery wheel may comprise such a heat exchange matrix in the form of a laminated sheet, the wheel has an axis aligned with the flow direction and, furthermore, comprises a fan arrangement for passing the air flow in the axial direction through the die, whereby the bands are provided on their surface by a desiccant material.

In this context, it should be noted that a desiccant material is different from a material that is only for water retention to the extent that it can retain water through additional hygroscopic or chemical mechanisms.

Therefore, a distinction can be made with non-desiccant water retention materials that retain water merely by phenomena of surface or physical stress.

Brief description of the drawings

[0035] The features and advantages of the invention will be appreciated in reference to the following drawings of a number of exemplary embodiments, where:

Figure 1 shows a conventional adiabatic humidifier;

Figure 2 shows a close-up view of part of the device of Figure 1;

Figure 3 shows a portion of a thermal exchange matrix, according to the present invention;

Figure 3A shows a detailed view of part of the matrix of Figure 3;

Figure 3B shows a cross-sectional view taken in the Illb position in Fig. 3A Figure 4 shows a sheet according to a second embodiment of the invention;

Figure 4A shows a partial view of the sheet of Figure 4 taken in the direction of arrow A Figure 5 shows an embodiment of the invention in the form of a heat recovery wheel;

Figure 5A shows a partial view of the matrix of Figure 5;

Figure 6 shows an embodiment of the invention as an adiabatic refrigerator element; and Figure 6A shows a partial view of the matrix of Figure 6.

Description of illustrative embodiments

[0036] Fig. 1 shows an arrangement of a conventional adiabatic humidifier 1 arranged to introduce moisture into an air stream S. The humidifier comprises a thermal exchange matrix 2 supported by a housing formation 4 forming an inlet 6 and an outlet 8 for the air stream S. In addition, a controller 10, a water supply 12 and a fan 14 are provided.

[0037] Fig. 2 shows a close-up of a section of the thermal exchange matrix 2.

It comprises a plurality of layers 20 of corrugated material comprising cellulose fibers impregnated with resin.

The layers 20 are stacked together, whereby the corrugations 22 in adjacent layers cross each other about

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flow passages that form angle 24.

The separation of the corrugations is about 25 mm.

[0038] A humidifier 1 as shown in Fig. 1 and Fig. 2 can be used to relatively cool, heat air to close to its wet bulb temperature.

In use, the air stream S to be cooled is supplied to the inlet 6.

In this phase, the air can have a temperature T1 and have low relative humidity RH1.

Water is supplied to the matrix 2 by the water supply 12 causing the fibrous material of the layers 20 to fill with moisture.

As the air stream S passes through the flow passages 24, it draws moisture from the surfaces of the layers 20 that evaporates in the air stream S. In this way, the air temperature is reduced and, consequently , its relative humidity increases.

The air stream leaves matrix 2 with a temperature T2 and a relative humidity RH2.

If enough aqueous vapor evaporates, the air will reach its wet bulb temperature and will be completely saturated with a relative humidity of 100%.

Although not shown, a droplet remover can be placed downstream of the matrix 2 to remove fine water droplets that may otherwise be carried by the air stream S.

[0039] Conventional humidifiers as described above are relatively bulky.

To achieve maximum humidification, the length in the flow direction is generally between 200 mm and 300 mm, depending on the typical humidity conditions of the incoming air.

The required frontal area is dependent on the desired capacity and requires about 0.14 m2 per 1000 m3 / h.

[0040] Fig. 3 shows a portion of a thermal exchange matrix 30, according to the present invention.

The matrix comprises a first sheet 32 and a second sheet 34.

The sheets 32, 34 each define a main plane P with a flow direction F and a transverse direction T.

By the following description, a non-deformed edge region of the sheets will be taken as the reference level for the prindpal plane P. Each sheet is divided into bands 36 that are partially separated from the sheets 32, 34 by cuts 38 and that are compensated from the main plane by a compensation distance d.

[0041] In the embodiment of Figure 3, the bands 36 are located in a plurality of rows 40 aligned in the flow direction F.

Consecutive bands in a row 40 are designated as 36a, 36b and 36c.

Fig. 3A shows a view of the matrix 30 of Figure 3, taken in the direction A.

As can be seen, the bands 36 are compensated for three different positions, that is, the zero position (located in the plane P) and at a distance d1 on the plane and a distance d2 below the plane.

Thus, each band 36 is separated from a neighboring band in the direction of flow F and compensated from the main plane P by a distance that is different from that of its neighbor.

[0042] Between each row 40, a free zone of band 42 is located which is also at the level of the main plane P. The spacers 44 are located in the free zones of band 42, in this case, in the center and in the matrix edges.

The spacers 44 serve to keep the sheets 32 and 34 at a distance from each other.

In the present embodiment, the distance d1 is 2.0 mm as is the distance d2.

The separation of the sheets 32, 34 is 6.0 mm.

In addition, the width w of each band 36 measured in the flow direction F is 2.0 mm and the length l of the bands 36 is 10 mm.

[0043] Fig. 3B shows a cross-sectional view of the sheet material 32 taken in position B in Fig. 3. Although the sheet 32 is described, it is understood that the sheet 34 is substantially identical.

The sheet 32 comprises a primary layer 46 of soft ringed aluminum with a thickness of 70 microns.

On each surface, the primary layer 48 is coated with a protective layer 50 of PVC primer or the like.

The protective layer 50 is also heat-sealable and can be used to join sheet parts together or for other elements during construction, if required.

The outermost layer on both surfaces of the sheet 32 is a water retention layer 52.

It should be noted that the thickness of these layers is shown schematically and, in fact, can vary considerably relative to each other.

[0044] An important factor for the effective operation of a vaporizable refrigerator is the nature of the water retention layer 52.

Although reference is made to a water retention layer, it is clearly understood that the layer, in fact, is a water retention and release layer, without chemically bonding it.

A requirement of such a layer is that it easily leaves its water, so that a minimum resistance to evaporation is found.

It is also important that it should distribute water quickly and efficiently to all surfaces

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relevant.

Thus, it should be hydrophobic without being hygroscopic, preferably, keeping the water mainly due to surface tension effects.

[0045] In the present embodiment, the water retention layer 52 is formed from a fibrous material. An exemplary material for the formation of the water retention layer 30 is a 20g / m2 polyester / viscose 50/50 mixture, available from Lantor B.V. in the Netherlands.

Another exemplary material is a polyester fiber coated with 30g / m2 of polyamide available under the name of Colback ™ from Colbond N.V. in the Netherlands.

Other materials that have similar properties, including synthetic and natural fibers, such as wool, can also be used.

Where necessary, the water retention layer 52 may be coated or otherwise treated to provide anti bacterial or other anti-contamination properties.

[0046] The water retention layer 52 is fixed by adhesive to the protective layer 50, using a 2 micron layer of two component polyurethane adhesive.

The resulting laminate has been found to be ideal for manufacturing purposes, since it can be formed and cut as desired in a continuous process without substantial delamination.

Other layers of water retention can also be used, such as Portland cement and although, in fact, it has been found that so far they provide superior properties, their production is more complex since there is a tendency to crack or peel, if applied before of the formation of the matrix.

However, it is believed that another surface ends and that the same treatments such as aluminum oxide may be suitable for the provision of the required water and wick retention.

[0047] In use, the matrix 30 can be provided in a block comprising multiple layers and can be placed in a housing 4, as described in relation to Fig. 1, taking the position of the conventional matrix 2. According to the Invention, the total size of the housing for a given cooling and the air flow can be reduced or, alternatively, a considerably higher air flow can be provided for a housing of the same size.

[0048] Fig. 4 shows a second embodiment of the invention, where the type of numbers preceded by 100 is used to designate elements similar to those of the first embodiment.

Sheet 132 defines a main plane P with a flow direction F and a transverse direction T.

In this embodiment, sheet 132 is divided into bands 136A-J separated from each other in the flow direction F by cuts 138 and into adjacent bands 136 in the transverse direction T by free zones of band 142.

Each band 136 has a corrugated contour comprising a first portion 135A-J offset for one side of the plane P and a second portion 137A-J is offset for the opposite side of the plane or is in the same plane (zero compensation).

In all, the band parts 135, 137 are compensated for 9 different positions with respect to the main plane P. Each band portion 135, 137 is compensated for a different position with respect to a neighboring band portion 135, 137 in the direction of flow F.

The band material is the same as described in relation to Fig. 3.

[0049] Fig. 4A shows a partial view of a portion of the sheet 132 of Figure 4 taken in the direction of arrow A where the different band portions 135 A-J, 137 A-J can be clearly seen.

As a result of the band portions 135, 137 being compensated for different positions, it can be achieved that each of the bands 136 has the same absolute length L as measured along its contour.

This has the advantage that when the bands 136 are cut from a continuous sheet, in general, there will be a relatively small deformation of the sheet and the band-free zones 142 will extend in a straight line.

[0050] Fig. 5 discloses an embodiment of the invention, where sheet 132 is shaped as a heat recovery wheel 160.

The sheet 132 is continuously wound to form a matrix 130 in the form of a roll.

Matrix 130 is supported within a housing 104 for rotation by a motor 107.

The flow takes place through the wheel in both directions Ff forward and Fr.

[0051] Fig. 5A shows a partial view of the matrix 130 of Fig. 5.

In this embodiment, the consecutive layers of the sheet 132 extend on top of each other without spacers in between.

Due to the numerous different compensations of the band portions 135, 137, the sheets 132 are effectively distanced from each other by the interaction of band portions of the neighboring layers.

It should also be noted that the band-free zones 142 are not located on top of each other, whereby the band-free zone in each adjacent layer forms a partial channel for air flow.

5

10

fifteen

twenty

25

30

35

40

Four. Five

[0052] In addition, in the embodiment of Figure 5A the water retention layer (not shown) is a desiccant coating of the type generally used for desiccant wheels.

This layer may be, for example, a type X or type Y, zeolite, silica, alumina or a mixture thereof with a modified isothermal behavior or any other suitable material as described for this purpose in US 5860284, the content of which is incorporated here by reference in its entirety.

In use, the wheel 160 of Figure 5 can operate in the same manner as a conventional desiccant wheel with the advantage of a relatively low pressure drop for a given size of the wheel 160 and flow rate.

[0053] Figure 6 shows an embodiment of the invention as an adiabatic refrigerator element 201 comprising a matrix 230 as described above retained by a housing 204.

A water distribution channel 212 along the upper side of the element 201 provides water passage holes 213 flowing down along the bands 236.

Water can be supplied to channel 212 by a suitable pump or other system.

The air flow in the flow direction F helps in the transport of water through the matrix 230. Additionally, the presence of the water retention layer covering the sheets 232 stimulates the water wick to all regions of the matrix 230.

The sheets 232 are spaced apart from each other by points of white material 244 comprising a PU adhesive foam.

Example

[0054] A matrix was constructed and evaluated as described above according to Fig. 4.

Similar tests were performed on a conventional CELDEK ™ 5090-15 matrix material available from Munters AB.

It should be noted that the material surface area per unit volume is comparable for both materials. The tests were performed according to an Australian standard (AS 2913-2000), whereby the supply air has a dry bulb temperature of 38 ° C and a wet bulb temperature of 21 ° C (21% relative humidity).

Saturation efficiency is the reduction of the actual supply air temperature (T inside - T outside) with respect to the temperature drop that would be required to reach the wet bulb temperature (T wet bulb inside).

Saturation efficiency = (T inside - T outside) / (T inside- T bulb wet inside)

[0055] The results provided in table 1 below show:

• For the same flow rate and volume, as the example, the comparative material has a 9% lower wet bubo efficiency and a 89% higher pressure drop;

• If the length of the comparative material increases to achieve the same efficiency at the same flow rate, as the example, 44% more material is required and the pressure drop will be 164% higher;

• With the same length, as the example, the flow rate for the comparative material must be reduced to around 1.8 m / s to achieve the same pressure drop.

For this 39%, more material in volume is required and the efficiency of wet bolt is 6% lower;

• If the length of the comparative material increases and the flow rate is adjusted, so that the pressure drop and wet bulb efficiency are comparable to those in the example, 122% more volume material is required.

Table 1

 Length mm Flow rate m / s Relative volume% Wet bubo efficiency% Pressure drop Pa Area area / vol m2 / m3

 Example

 90 2.5 100 90 53 652

 Comparative material - same length and flow rate

 90 2.5 100 81 100 588

 Comparative material - same efficiency and flow rate

 130 2.5 144 90 140 588

 Comparative material - same length and descent P

 90 1.8 139 84 53 588

 Comparative material - same efficiency and lowering P

 120 1.5 222 90 53 588

[0056] Thus, the invention has been described by reference to certain embodiments, as mentioned above.

It will be recognized that these embodiments are susceptible to various modifications and alternative forms well known to those skilled in the art.

[0057] In addition to the modifications described above, many others can be made to the structures and techniques described herein without departing from the scope of the claims.

Therefore, although specific embodiments have been described, these are only examples and are not limiting on the scope of the claims.

Claims (15)

5 10 fifteen twenty 25 30 35 40 Four. Five fifty 55 60 65 1. Vaporizable refrigerator, adiabatic refrigerator or humidification unit comprising: a thermal exchange matrix (30) defining a single flow channel and comprising a plurality of generally flat sheets (32, 34) comprising a water retention material, a distantly arranged relationship, substantially parallel and a plurality of spacers (44) located between adjacent sheets to maintain their distance relationship, each sheet defines a main plane with a flow direction and a transverse direction, a housing (4) with at least one air inlet (6), an air outlet (8), the array located in the housing; a fan arrangement (14) for directing air through the die in the flow direction; and a water source (12) for the humidification of the matrix, characterized in that the sheets comprise bands (36) that extend in a band length in the transverse direction and are separated from each neighboring band in the flow direction and each band is compensated from the main plane by a distance that is different from that of your neighbor. 2. Device according to claim 1, wherein the bands are compensated for the front and rear positions of the main plane, preferably at least four different positions. 3. Device, according to claim 1 or claim 2, wherein the bands are generally parallel to the main plane. 4. Device, according to any preceding claim, where each band is partially compensated for a first position and partially compensated for a second position. 5. Device according to any one of the preceding claims, wherein each band has a width in the flow direction and a first band is distanced in the flow direction from a subsequent band with the same compensation by at least three times the width , more preferably at least five times the width. 6. Device according to any one of claims 1 to 5, wherein the bands are arranged in a plurality of rows extending in the flow direction, each row is separated from an adjacent row by a band-free zone and the spacers preferably They extend along the band-free zones. 7. Device according to any of the preceding claims, wherein the water retention material comprises a water retention layer applied to the bands, preferably, on both surfaces thereof. 8. Device according to any of the preceding claims, wherein the bands have a width of between 1 mm and 5 mm, preferably between 1.5 mm and 3.0 mm. 9. Device according to any of the preceding claims, wherein the sheet is between 50 and 300 microns thick, preferably between 75 and 150 microns, and preferably comprises an aluminum layer. 10. Device according to any of the preceding claims, wherein the thermal exchange matrix comprises a plurality of sheets of similar dimensions stacked together to form a block as a structure. Device according to any one of claims 1 to 10, wherein the thermal exchange matrix comprises one or more rolled sheets joined to form a cylindrical or annular structure. 12. Device according to any of the preceding claims, wherein a spacing between adjacent sheets is between 1 mm and 5 mm, preferably between 1.5 mm and 3.0 mm. 13. Method of manufacturing a device according to any one of claims 1 to 12, comprising: providing a supply of sheet material with first and second water retention surfaces; passing the sheet material through a cutting station to cut the sheet to form a plurality of bands, each band has a band length that defines a transverse direction and each band is separated by the cut of each neighboring band in a direction flow; pass the cutting blade through a training station to compensate each band of a main plane of the blade for a distance that is different from that of its neighbor; separate sheet sections and stack the seccones to form a stack with multiple layers or roll the sheet to form a roll with multiple layers; and insert spacers between multiple layers to maintain their respective spacings while maintaining a single channel. 14. Adiabatic refrigerator according to any one of claims 1 to 12, wherein the bands generally extend vertically and the flow channel generally extends horizontally, the water source is arranged to supply water on an upper side of the plurality of sheets, so that water can flow down along the bands. 15. Adiabatic refrigerator, according to claim 14, wherein the sheets are spaced apart by spacers 5 with limited extension in the flow direction, preferably, comprise polymer material points with a dimension in the main plane of the sheets of less than 1 cm.